Closing force unit

ABSTRACT

A closing force unit for the treatment space of a tire vulcanization machine, having a base plate and at least one linear drive for the displacement and force application of a mold pressure plate, wherein the at least one linear drive is an integral part of the base plate so that a compact and stringent structure of the closing force unit is supported. A tire vulcanization machine having such a closing force unit.

The invention relates to a closing force unit for the treatment chamberof a tire vulcanization machine, having a base plate and at least onelinear drive for the displacement of and exertion of force on a moldpressure plate.

The invention also relates to a tire vulcanization machine having aclosing force unit of said type.

The production of a tire, for example for vehicles such as automobiles,heavy goods vehicles or motorcycles, is an extremely complex processmade up of a multiplicity of production and process steps. A reason forthis is the complex tire structure composed of a considerable number ofdifferent individual components. Furthermore, said multiplicity ofcomponents must be connected to one another under the action of pressureand temperature, through so-called vulcanization. The vulcanizationprocess is likewise of significance with regard to the material and gripcharacteristics of the finished tire.

For this reason, one of the main production steps for the production oftires is the vulcanization of green tires to form a finished tire. Forthis purpose, the green tire is placed into a mold or tire mold which issituated within a tire vulcanization machine and which is subsequentlyheated to the material-dependent vulcanization temperature and chargedwith a vulcanization pressure at the inside of the green tire. To attainthe vulcanization temperature and the vulcanization pressure, a suitableheating medium is introduced, with corresponding exposure to temperatureand pressurization, into the interior space of the green tire.

The vulcanization basically has the aim of practically “baking” a greentire “into a finished state” by exposure to temperature andpressurization within one or more time intervals, that is to sayconnecting the components of the green tire to one another and impartingelastic characteristics to the base materials and to the rubber layer bycross-linking processes. For this purpose, aside from the actualpressurization and exposure to temperature, various additive substancesadapted to the base material are also required for the cross-linking andpossibly for accelerating the cross-linking.

To carry out a vulcanization of the elastomer material, a considerablequantity of heat energy must be introduced into the material. For thispurpose, it is in most cases not sufficient for the green tire forvulcanization to be exposed to a vulcanization temperature, andpressurized with a vulcanization pressure, from the inside.

To realize the quantity of heat energy and pressurization required forthe vulcanization process, provision is alternatively or additionallymade for the green tire to be subjected to pressure and/or action oftemperature at the outside of the green tire in the vulcanizationmachine. For this purpose, it is normally the case that a treatmentchamber is installed, which is referred to as tire mold and which can beopened and closed such that the green tire for vulcanization can beplaced in, vulcanized and removed.

Particularly thick regions of the green tire are the treads. The sidewalls are of relatively thin form. This considerable thicknessdifference arises owing to the additional tire components arranged inthe region of the tread, such as steel belts, belt cover ply and therubber layer which is considerably thicker than the side wall. Saidconsiderably thicker rubber layer has a greater wall thickness not leastbecause it comprises the tire profile itself, which is produced duringthe vulcanization process. For this purpose, the tread region, or thethick-walled rubber mass provided there, must be heated to such anextent that it can plastically flow and can be pressed by thevulcanization pressure into the profile negative die of the green tiremold of the tire vulcanization machine. The plastic flow capabilityincreases over a broad range with increasing heating of the material,such that less pressing pressure is required to be able to reliablyproduce the profiling.

Following the general physical principle of omnidirectional pressurepropagation, the treatment chamber, that is to say the tire mold, mustsupport and accommodate the pressing and pressure forces both in aradial direction and in an axial direction. As a result, regardless ofwhether the tire mold longitudinally or transversely with respect to theaxis of rotation of the tire for vulcanization, the movement devices foropening and closing the tire mold must normally not only impart theforces for moving at least one mold half but also be adequatelydimensioned with regard to the closing forces during the tirevulcanization. Owing to the closing forces, which may reach several kN,use is normally made of high-pressure fluid cylinders in addition tomechanical solutions such as for example knee lever structures orspindles.

DE 10 2014 001 643 A1, for example, presents a tire heating press ortire vulcanization machine of frame-type construction with afunctionally separate two-component solution with regard to the verticalpositioning and the accommodation of closing force. It is disclosed thatthe adjustment of the height of the mold is realized by means of atleast two double-acting hydraulic cylinders and at least one guideelement, wherein the guide element has at least one position securingfacility by means of at least one locking device and can therebyaccommodate the closing forces.

To realize the adjustment of the height of the mold within the tireheating press, the height of at least one mold half is effected by meansof at least two hydraulic cylinders. The introduction of energy isrealized by means of the pressurized liquid volume flow in a knownmanner by virtue of said pressurized liquid volume flow being introducedinto the fluid cylinder through feed lines.

The fluid cylinders are configured as separate, installation-ready unitsand are normally purchased parts. Owing to the considerable longitudinalextent of installation-ready fluid cylinders, said components must bearranged within the machine bed and have an adverse effect on, that isto say increase, the structural height of the machine frame and the tirevulcanization machine as a whole.

The teaching of DE 10 2014 001 643 A1 combines the fluid cylinders forthe adjustment of the height of the mold of a tire heating press with atleast one guide element. Said guide element is preferably mountedcentrally with respect to the height-adjustable mold halves and/orcentrally with respect to the fluid cylinder arrangement and designedfor accommodating radial and axial forces. With the use of the at leastone guide element, the radial forces are not introduced into the fluidcylinder, and damage, for example leaks, is/are prevented.

The guide element is furthermore equipped with a locking device. Saidlocking device enables the entire structural element composedsubstantially of the fluid cylinders, the mold half and the guideelement fixed to the mold half to be fixed in an axial-linear movementdirection. It is achieved in this way that, after the fluid cylindershave adjusted the mold half into the desired height position and thelocking device has been activated, the fluid cylinders can be switchedinto an unpressurized state. This means that the linear forces in anaxial direction that act within the press during the tire productionprocess, that is to say the closing forces themselves, are accommodatednot by the fluid cylinders but by the guide element.

Another solution consists in the closing forces being accommodated notby a guide element but rather directly via the fluid cylinders, withoutthe use of a guide element. In this case, however, the fluid cylindersmust be designed for the very high closing forces. Furthermore, theoccurring radial forces must be accommodated by the piston rods andpiston-rod guides of the fluid cylinders.

Both design variants for realizing the accommodation of the closingforces are basically usable both in frame-type presses and incolumn-type presses or in tire vulcanization machines constructed onstands, but in any case require correspondingly adequate dimensioning.

The known closing force units have numerous disadvantages which mayexist both individually and collectively. Although fluid cylinders whichcan be purchased as installation-ready units are in themselvesinexpensive, the outlay in terms of construction for integration intothe tire vulcanization machine, and the resulting increased machinestructural height, are however considerably expensive and elaborate.

Furthermore, forces acting radially on the fluid cylinders can have ahighly adverse effect on, that is to say can shorten, the service lifeand/or the sealing action thereof. Purchasable fluid cylinder structuralunits are normally not suitable and designed, or are suitable anddesigned only to a limited extent, for absorbing radial forces. Thehigher costs resulting from the construction of a radial forceaccommodating device that is required as a result increase the generaloutlay in terms of construction, and can impede or adversely affect theaccessibility to the press elements in said region.

A further problem may arise from the fact that the fluid cylinderstructural units are generally accommodated within the machine bed. Thereceiving bores, leadthrough openings and fastening means and partiallyrequired cutting-out of reinforcement ribs have the effect of reducingstrength with regard to the overall structure, and can result inincreased deformation of the load-bearing unit.

A problem addressed by the invention is that of providing a closingforce unit for tire vulcanization machines which at least partiallyreduces the stated disadvantages and supports an inexpensive overallconstruction.

To solve said problem, the teaching according to the invention proposesthat at least one fluid cylinder is formed as an integral constituentpart of the tire vulcanization mold and/or of the machine components.

As an approach to a solution, it is provided that the fluid cylindercomposed of piston and possibly piston rod and cylinder housing is notintroduced as a separate purchased part, with provision rather beingmade for a fluidic linear drive to be constructed integrally in the baseplate of the tire vulcanization machine.

The integral design is realized by the invention through the directutilization of the base plate as a cylinder housing. For this purpose,bores are formed into the base plate in accordance with the requirednumber of fluidic linear drives, which bores may, depending on theembodiment of the fluidic linear drive, be formed as passage boresand/or as blind bores. In this way, both piston-piston rod linear drivesand also piston-type linear drives based on the plunger cylinderprinciple can be integrated.

In a preferred embodiment, the invention provides linear drives based onthe plunger cylinder principle integrated into the base plate. For thisconstruction, blind bores are provided in the base plate, which blindbores correspond in terms of their bore diameters to the respectivelyused piston and provide a clearance fit which supports linear mobilityof the piston in the bore. The pistons or blind bores may have sealeddevices such as for example bushings, piston rings, stripper rings orSimmerrings in order to reduce the escape of fluid from the concentricring-shaped movement gap between piston and blind bore.

In particular, the linear drives integrated into the base plate haveconsiderable advantages in relation to known closing force units:

-   -   Through the utilization of the base plate as a cylinder for the        pistons, separate cylinders are not required and thus save        costs, and furthermore    -   the structural space situation is advantageous from numerous        aspects simultaneously in that both a reduced overall machine        height and the compact piston arrangement and an optimally        utilizable base plate surface are supported,    -   owing to the sealed piston arrangement, very uniform and        homogeneous introductions of closing force into the tire mold        are possible,    -   the machine bed can be designed optimally from a strength aspect        without the receiving spaces and bores for fluid cylinders,    -   the available piston surfaces can realize considerable closing        forces even without fluid pressures in the high-pressure range,        such that expensive and energy-intensive high-pressure        apparatuses for the build-up of fluid pressure can be omitted,        and operation in the low-pressure range below 100 MPa,        preferably at approximately 40 MPa, is supported,    -   the time required for the build-up of the closing force is        minimized,    -   the large piston diameters of the linear drives support the        accommodation of radial forces,    -   the considerably large piston surfaces of the solution according        to the invention result in a reduced contact pressure between        the respective piston face surface and the mold pressure plate        or the tire mold, such that the temperature insulating means        required at these locations are subjected to lower mechanical        load, with the result that    -   a less expensive material and/or a material with improved        insulation capabilities can be used for the temperature        insulation means, and    -   the energy efficiency of the tire vulcanization machine as a        whole is increased owing to the resulting reduced heat energy        losses.

By means of the construction according to the invention of the closingforce unit with linear drives integrated into the base plate, costsavings can be achieved which amount to up to 70% of the costs ofsimilar solutions with separate linear drives in the form of purchasedparts. For the integration of the linear drives into the base plate, itis envisaged that the plate thickness of said base plate be increased byup to 150%, such that a thickness of approximately 250 to 300 mm isrealized.

As a result of the integration of the at least one linear drive as afunctional constituent part of the base plate, a compact stringentstructure of the closing force unit is realized according to theinvention, which as a result offers considerable cost saving potentialand has the stated functional improvements.

One of the possible embodiments of the closing force unit according tothe invention for tire vulcanization machines, having at least onelinear drive integrated into the base plate, is illustrated in figures,in which:

FIG. 1 shows an exemplary embodiment of the closing force unit (1)according to the invention for tire vulcanization machines (200) in aperspective overall illustration of the tire vulcanization machine (200)with a partial section in the x-z plane,

FIG. 2 shows the perspective sectional illustration of the vulcanizationchamber or of the tire mold (30) with closing force unit (1), and

FIG. 3 shows the perspective sectional illustration of the closing forceunit (1) in a detail view.

FIG. 1 illustrates a tire vulcanization machine (200) with an exemplaryembodiment of the closing force unit (1) according to the invention in athree-dimensional overall view. The tire vulcanization machine (200),which is also referred to as tire heating press, is in this exampleconstructed as a column-type press and, in its load-bearing overallconstruction, has a machine bed (100) with columns (110), a crossmember(80) and a base plate (10).

If the tire heating press is constructed for example as a frame-type orstand-type press, the closing force unit (1) may be integrated into themachine frame or, as in the case of the column-type construction shownin FIG. 1, into a base plate (10). In this way, the closing force unit(1) according to the invention can be realized independently of the typeof construction of the press and in any desired tire vulcanizationmachine (200).

A functional core element of the tire vulcanization machine (200) is thetreatment chamber or the vulcanization chamber/tire mold (30), thespatial extent of which is delimited by the mold pressure plate (40) andby the mold counterpressure plate (60) and by a preferably cylindricaltension casing (50). Aside from the delimitation of the vulcanizationspace (30), the tension casing (50) is assigned two further functionaltasks: owing to the pressure forces within the vulcanization chamber(30) during the vulcanization of the green tire, the tension casing (50)accommodates the resultant (tensile) forces in an axial direction, andhas an insulating action with regard to the vulcanization temperaturesof up to 160 degrees Celsius, in some cases even higher, which prevailin the vulcanization chamber (30).

The mold pressure plate (40) can be linearly axially both displaced andalso subjected to force, both being introduced into the mold pressureplate (40) by the closing force unit (1), such that a pressing force canbe built up in the vulcanization chamber (30) and the volume thereof canbe set. The mold counterpressure plate (60) practically constitutes thecounterbearing, with respect to the mold pressure plate (40), for theclosing and pressing forces, wherein the tension casing (50) producesthe force-transmitting connection between the plates (10, 40, 60).

The tension casing (50) is preferably fixed to the mold counterpressureplate (60) and axially movable as a common structural unit. The moldcounterpressure plate (60) is guided together with the tension casing(50), via a crossmember (80), by two columns (110). The axial movementdrive for the structural unit of mold counterpressure plate (60) withtension casing (50) is realized by means of two fluid cylinders (90)which produce an operative connection of crossmember (80) to machine bed(100) and which are preferably of double-acting form.

FIG. 2 shows, in a perspective sectional illustration, the region of thevulcanization chamber (30). Essential constituent parts of thevulcanization chamber (30) are the mold pressure plate (40), the moldcounterpressure plate (60) and the tension casing (50). Optional adapterplates (70) may be provided for fixing tire mold halves to the moldpressure plate (40) and/or to the mold counterpressure plate (60).

The closing force unit (1) is positioned adjacent to the vulcanizationchamber (30) such that both the closing force and the axially directeddisplacement travel can be introduced into the mold pressure plate (40).The example shown in FIG. 2 realizes the positioning of the closingforce unit (1) adjacent to the treatment chamber (30) by means of theconcentric position vertically below the mold pressure plate (40).

If devices for internal pressurization and applying heat energy to thegreen tire to be vulcanized are required in the tire mold or thevulcanization chamber (30), passage regions (11, 41, 61) may be providedfor the leadthrough of the mechanical components.

To realize the closing force unit (1) according to the invention in theembodiment and arrangement example shown, at least one piston (20) isarranged in the base plate (10) such that said piston, as an integratedlinear drive (5), can displace and exert force on the mold pressureplate (40). It is particularly advantageous for multiple pistons (20) tobe used in a manner distributed symmetrically or asymmetrically on theface side of the base plate (10). It is possible for four or morepistons (20) to be installed such that,

-   -   firstly, the available base plate area is optimally utilized,        and/or    -   a highly uniform contact pressure and introduction of force can        be introduced by the multiple pistons (20) into the mold        pressure plate (40), and/or    -   the axially linear displacement can be introduced substantially        uniformly into the mold pressure plate (40), and in this way,        misalignment or tilting of the base plate (10) during the        displacement is reduced, and/or    -   a large effective total piston surface area is provided across        the pistons (20) used, such that a reduced contact pressure        prevails between the respective piston face surfaces and the        mold pressure plate (40), and the temperature insulation means        required at said locations are subjected to lower mechanical        load, and/or even the low pressure range of the fluid results in        adequately high pressing forces.

FIG. 3 shows the exemplary embodiment of the closing force unit (1) fromFIG. 1 and FIG. 2 in a perspective sectional illustration. The baseplate (10) is equipped with each case one blind bore (12) foraccommodating the piston (20). The bore diameter realizes a clearancefit with the piston diameter, such that the piston (20) is displaceablein its axial direction in the blind bore (12) when a fluid, such as forexample water or hydraulic oil, is introduced into the fluid chamber(13). The fluid chamber (13) is defined and delimited at the base plateside by the blind bore base and by the bore wall, and the piston crown(21) as a displaceable element closes off the fluid chamber (13) with athereby variable volume.

As an alternative to the blind bore (12) shown in FIG. 3, the pistonreceptacle in the base plate (10) may also be realized by a passage borewhich is closed off on one side by a plate after the production process.In this case, the fluid chamber (13) is defined and delimited by theplate and by the bore wall.

To introduce the fluid into and/or discharge said fluid from the fluidchamber (13), the invention provides at least one opening in the baseplate (10), which opening is preferably formed as a bore at the blindhole base (not shown) and supports the connection to a fluid apparatus.Alternatively or in addition, the at least one opening may be arrangedon the bore wall or on the piston (20).

Owing to the considerable utilizable piston surfaces, the closing forcesthat result from the contact pressures may, even in the case of fluidpressures in the low pressure range, be high enough that the fluidiclinear drives (5) and fluid apparatuses do not have to be realized inthe expensive high-pressure variants.

According to the invention, the piston construction may be realizedoptionally as a plunger-type piston or as a piston-piston rod unit.

In terms of geometry, the plunger-type piston is a prismatic, preferablycylindrical piston with a continuous shell without a shoulder. In otherwords: the plunger-type piston has no piston rod, and the piston extendsover the entire axial length and functionally also performs the task ofthe piston rod. Owing to this design, the plunger-type piston can beproduced very easily and, together with the receiving bore in the baseplate (10), forms a clearance fit gap which, owing to its very largemeridian length, both has excellent sealing characteristics and guidesthe plunger-type piston in a very exact manner.

The piston structure of the piston-piston rod unit has a piston region(20′) and a piston rod region (20″) with an interposed shoulder in theform of a concentric diameter step. The diameter in the piston region(20′) is larger than the diameter in the piston rod region (20″), suchthat only the meridian length of the piston region (20′) forms aclearance fit gap together with the receiving bore (12) in the baseplate (10). Owing to the second fluid chamber which is thus formed andwhich is bordered by the bore wall, the concentric diameter step and theouter wall of the piston rod region (20″), the linear drive (5) can beof double-acting design.

To reduce the escape of fluid from the clearance fit gap, the inventionprovides at least one seal (14), assigned in each case to a linear drive(5) of the closing force unit (1). The seal (14) may for example be anO-ring or a Simmerring. Furthermore, a stripper ring (15) may beprovided which interacts with the seal (14).

The positioning of the seal (14) and of the stripper (15) may berealized in a variety of configurations: in the example shown, a ring(16) is reversibly fixed to the base plate (10) at the piston outletside of the bore (12) and is equipped, on the inside, with correspondingring-shaped grooves for receiving the seal (14) and the stripper (15).If no ring (16) is used, the grooves, and thus the positioning of theseal (14) and the stripper (15), may be arranged for example within thebore (12) and/or in the piston side surface.

The ring (16) may optionally have further structural and functionalfeatures. For example, a collar may be formed thereon, which collarprojects into the bore (12) and is formed as a bushing. Furthermore, thering (16) may functionally act as a stop with the shoulder of the piston(20) between the piston region (20′) and the piston rod region (20″) andthereby limit the linear deployment movement of the piston (20).

On the face side of the piston (20) and adjacent to the mold pressureplate (40), there is normally a need for temperature insulation measuresfor reducing the heat transfer into the at least one piston (20) andbase plate (10) from the vulcanization chamber (30).

Owing to the very large piston face surface provided by means of theteaching according to the invention, and the altogether large contactsurfaces of the multiple pistons (20) that are preferably used, thecontact pressure that acts on the contact surfaces is relatively low,despite high closing forces that can be realized by the closing forceunit (1). The reduced contact pressure in said regions supports the useof temperature insulation elements (17) with low compressive strengthcharacteristics. As a result, use may be made of insulation materialswhich are less expensive and/or exhibit improved insulationcharacteristics.

The temperature insulation elements (17) may, by means of differentthicknesses, simultaneously be utilized for compensating shape anddimensional tolerances and thereby leveling height differences in thecase of multiple linear drives (5) being used.

1-20. (canceled)
 21. A closing force unit for a treatment chamber of atire vulcanization machine, comprising: a base plate; and at least onelinear drive for displacement of and exertion of force on a moldpressure plate, wherein the at least one linear drive is an integralconstituent part of the base plate, such that a compact stringentstructure of the closing force unit is supported.
 22. The closing forceunit according to claim 21, wherein the at least one linear drive is apiston that is received in movable fashion in a bore of the base plate.23. The closing force unit according to claim 22, wherein the piston isa plunger piston.
 24. The closing force unit according to claim 22,wherein the piston is a piston-piston rod combination having a pistonregion and a piston rod region.
 25. The closing force unit according toclaim 24, wherein a transition between the piston region and the pistonrod region is formed by a concentric diameter step.
 26. The closingforce unit according to claim 22, wherein the bore is a blind bore. 27.The closing force unit according to claim 22, wherein the bore is athrough bore.
 28. The closing force unit according to claim 22, whereinthe bore and the piston are formed so that a clearance fit gap isrealized between them, so that the piston is received in movable fashionin the bore of the base plate.
 29. The closing force unit according toclaim 28, wherein the clearance fit gap is a concentric ring-shaped gap.30. The closing force unit according to claim 28, further comprising atleast one seal assigned to the linear drive so that an escape of fluidfrom the clearance fit gap is reduced.
 31. The closing force unitaccording to claim 30, wherein the at least one seal is an O-ring or ashaft seal.
 32. The closing force unit according to claim 28, furthercomprising at least one wiper assigned to the linear drive so as to wipefluid from a region of a wall of the piston that extends from the bore.33. The closing force unit according to claim 30, wherein the at leastone seal is assigned to the piston wail and/or to a wall of the boreand/or to a ring.
 34. The closing force unit according to claim 30,wherein the at least one wiper is assigned to the piston wall and/or toa wall of the bore and/or to a ring.
 35. The closing force unitaccording to claim 22, wherein a first fluid chamber is defined anddelimited at a base plate side by walls of the bore, and the piston hasa crown as a displaceable element that closes off the fluid chamber witha thereby variable volume.
 36. The closing force unit according to claim35, wherein the fluid chamber has at least one opening for anintroduction and/or discharge of fluid into and/or from the fluidchamber.
 37. The closing force unit according to claim 34, wherein thefluid is a hydraulic oil or water.
 38. The closing force unit accordingto claim 25, wherein an introduction of fluid into the fluid chamber isperformed under low-pressure conditions.
 39. The closing force unitaccording to claim 38, wherein the low-pressure condition lies below 100MPa.
 40. The closing force unit according to claim 39, wherein thelow-pressure condition is 40 MPa.
 41. The closing force unit accordingto claim 22, further comprising a temperature insulation dement on aface side of the piston.
 42. A tire vulcanization machine, comprising aclosing force unit according to claim 21.